Air inlet structure for compressor and compressor

Abstract

The embodiment of the invention relates to the technical field of compressor equipment, in particular to an air inlet structure for a compressor and the compressor, the air inlet structure comprises a horizontal split type air inlet section and a rigid supporting section, and specifically, the horizontal split type air inlet section comprises a first bearing box and a second bearing box which can be separated. The rigid supporting section is of an integrated cylindrical structure formed through integral casting or welding, and a plurality of adjustable guide vanes are arranged in the rigid supporting section in the circumferential direction. The inlet end of the rigid supporting section is fixedly connected with the outlet end of the flow guide cavity, and first rabbets which are embedded with each other are formed in the connecting interface between the rigid supporting section and the outlet end; through the connection mode, the rigid supporting section with high rigidity provides powerful radial supporting and axial limiting for the split type horizontal split type air inlet section; by means of the air inlet structure, the problem that a hydraulic pressure test of a traditional horizontal subdivision structure is difficult to pass under the high-pressure working condition is solved, and the operation safety and reliability of a compressor unit are remarkably improved.

Description

Inlet structure for compressors and compressor Technical Field

[0001] This application relates to the field of compressor equipment technology, and in particular to an intake structure for a compressor and a compressor. Background Technology

[0002] Horizontally split compressors are widely used in petrochemical, natural gas transmission, and energy storage fields due to their compact structure and convenient rotor disassembly and maintenance. The casing of this type of compressor is typically divided into upper and lower halves along a central split surface, connected by flange bolts. To optimize the intake flow and improve gas flow efficiency, some horizontally split compressors adopt a horizontal intake structure, meaning the intake chamber also uses a split design, manufactured integrally with or separately from the compressor main casing, to achieve axially uniform airflow into the impeller.

[0003] Currently, in energy storage and high-pressure applications, the intake section of some horizontally split compressors typically uses a traditional horizontally split structure. This intake section consists of upper and lower bearing housings joined together to form a flow guide chamber, which is directly connected to the compressor housing via a flange. To adjust the intake flow rate and adapt to different operating conditions, an adjustable guide vane mechanism is usually installed in this connection section or near the compressor inlet.

[0004] However, the aforementioned existing technical structure has the following drawbacks in practical application and production inspection: First, due to its structural limitations, the horizontally split intake section has significantly lower circumferential stiffness. Under high unit pressure or during hydrostatic testing, radial expansion within the intake chamber due to pressure can cause deformation of the split surface, leading to sealing failure and leakage. To solve this problem, repeated grinding of the split surface to ensure fit is necessary, and sometimes, with the user's consent, adding a sealing groove and applying sealant to the split surface to compensate for deformation defects is required. This approach not only prolongs the testing cycle but also increases manufacturing costs due to repeated grinding, severely impacting product delivery time. Summary of the Invention

[0005] The summary section introduces a series of simplified concepts, which will be further explained in detail in the detailed description section. This part of the invention is not intended to limit the key features and essential technical features of the claimed technical solution, nor is it intended to determine the scope of protection of the claimed technical solution.

[0006] The present invention aims to solve at least one of the technical problems existing in the prior art or related art.

[0007] To this end, a first aspect of the present invention provides an intake structure for a compressor, comprising: a horizontally split intake section, the horizontally split intake section including a separable first bearing housing and a second bearing housing, the first bearing housing and the second bearing housing being joined to form a guide cavity for intake; a rigid support section, the rigid support section being an integral cylindrical structure, the rigid support section having multiple guide vanes arranged circumferentially inside; the inlet end of the rigid support section being connected to the outlet end of the guide cavity, and a first stop being provided at the connection interface to fit together, so that the rigid support section provides rigid support for the horizontally split intake section.

[0008] In one feasible implementation, it further includes: a first flange disposed at the inlet end of the rigid support section; a second flange disposed at the outlet end of the guide cavity; the first stop includes a first convex stop disposed on the first flange, and the second flange is provided with a first concave stop that mates with the first convex stop.

[0009] In one feasible embodiment, the system further includes: a guide vane seat disposed on the inner side of the rigid support section, wherein a transmission cavity is formed between the outer periphery of the guide vane seat and the inner wall of the rigid support section; a plurality of first mounting holes disposed circumferentially along the guide vane seat, wherein the guide vane shafts of the plurality of guide vanes are rotatably disposed in the corresponding first mounting holes, and the ends of the guide vane shafts extend into the transmission cavity; a second mounting hole disposed on the side wall of the rigid support section; a drive shaft rotatably disposed in the second mounting hole, wherein the end of the drive shaft extends into the transmission cavity, wherein the drive end of the drive shaft is connected to one of the guide vane shafts, and the drive shaft is driven by a guide vane actuator; and a transmission assembly disposed in the transmission cavity, wherein the transmission assembly is respectively connected to all the guide vane shafts to drive all the guide vane shafts to rotate around their own axes when the drive shaft rotates.

[0010] In one feasible implementation, the transmission assembly includes: a plurality of bevel gears, respectively disposed on each of the guide vane shafts; and a bevel gear ring, sleeved on the outer periphery of the guide vane seat, wherein the bevel gear ring meshes with all of the plurality of bevel gears.

[0011] In one feasible implementation, the guide vane seat further includes a guide vane bushing, which is detachably disposed between the guide vane seat, the horizontally split intake section, and the rigid support section.

[0012] In one feasible implementation, the guide vane bushing and the guide vane seat are connected by a second stop; the second stop includes a second concave stop provided on the end face of the guide vane bushing, and also includes a second convex stop provided on the end face of the guide vane seat, the second concave stop and the second convex stop cooperating.

[0013] A second aspect of the present invention provides a compressor, the compressor including the air intake structure described above, and further including: a compressor main housing, the compressor main housing being connected to the outlet end of the rigid support section, and a mutually fitting third stop being provided at the connection interface; the third stop including a third convex stop provided on the end face of the compressor main housing, the outlet end of the rigid support section being provided with a third flange, the third flange being provided with a third concave stop, the third concave stop cooperating with the third convex stop.

[0014] In one feasible embodiment, the compressor main casing has a horizontally split structure, including a first casing and a second casing that fit together. A center-part flange is provided at the joint between the first casing and the second casing. A circumferential flange is provided at the outlet end of the compressor main casing, and the outer diameter of the circumferential flange is larger than the outer edge diameter of the center-part flange. A plurality of bolt holes are provided on the center-part flange, and the bolt holes are located near the root of the circumferential flange.

[0015] In one feasible implementation, the third flange is connected to the compressor housing by a plurality of circumferentially distributed bolts, and the fastening nuts of the bolts located in the guide vane actuator mounting area are type II hexagonal nuts.

[0016] In one feasible embodiment, the compressor further includes: a rotor disposed within the compressor main housing; the rotor having a smooth shaft section corresponding to the rigid support section for providing clearance space during axial advancement installation of the guide vane seat and / or the guide vane.

[0017] Compared with the prior art, the present invention has at least the following beneficial effects: The air intake structure provided in this application includes a horizontally split air intake section and a rigid support section. Specifically, the horizontally split air intake section includes a separable first bearing housing and a second bearing housing. The rigid support section is an integral cylindrical structure cast or welded, with multiple adjustable guide vanes arranged circumferentially inside. The inlet end of the rigid support section is fixedly connected to the outlet end of the guide cavity, and a first stop is provided at the connection interface between the two. Through this connection method, the high-rigidity rigid support section provides strong radial support and axial restraint for the split horizontally split air intake section. This air intake structure solves the problem that traditional horizontally split structures are difficult to pass the water pressure test under high pressure conditions, significantly improving the operational safety and reliability of the compressor unit.

[0018] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of the present invention more apparent and understandable, specific embodiments of the present invention are described below. Attached Figure Description

[0019] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings: Figure 1 is a schematic structural diagram of the intake structure according to the first embodiment of this application; Figure 2 is a structural diagram of the guide vane installation of the intake structure according to this application; Figure 3 is a detailed view of the guide vane installation of the intake structure according to this application; Figure 4 is a cross-sectional view of the guide vane drive of the intake structure according to this application; Figure 5 is a schematic diagram of the installation of the guide vane bushing on the intake structure according to this application; Figure 6 is a schematic structural diagram of the compressor according to the first embodiment of this application; Figure 7 is a schematic diagram of the bolt engagement of the compressor according to the first embodiment of this application; Figure 8 is a simulation diagram of the sealing effect of a conventional housing; Figure 9 is a simulation diagram of the housing sealing effect of the compressor according to this application.

[0020] The correspondence between the reference numerals and component names in Figures 1 to 9 is as follows: 1. Horizontally split intake section; 2. Rigid support section; 3. First stop; 4. First flange; 5. Second flange; 6. Guide vane seat; 7. Drive shaft; 8. Guide vane actuator; 9. Bevel gear; 10. Bevel gear ring; 11. Guide vane bushing; 12. Second stop; 13. Compressor main housing; 14. Third stop; 15. Circumferential flange; 16. Split-face flange; 17. Type II hexagonal nut; 18. Guide vane. Detailed Implementation

[0021] The following description provides numerous specific details to offer a more thorough understanding of the technical solutions provided by this invention. However, it will be apparent to those skilled in the art that the technical solutions provided by this invention can be implemented without one or more of these details.

[0022] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms “comprising” and / or “including” are used in this specification, they indicate the presence of the stated features, integrals, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components, and / or combinations thereof.

[0023] Exemplary embodiments according to the present invention will now be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments may be implemented in many different forms and should not be construed as being limited to the embodiments set forth herein. It should be understood that these embodiments are provided so that the disclosure of the invention is thorough and complete, and that the concept of these exemplary embodiments is fully conveyed to those skilled in the art.

[0024] To better understand the above technical solutions, the technical solutions of the embodiments of this application will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the embodiments of this application and the specific features in the embodiments are detailed descriptions of the technical solutions of the embodiments of this application, rather than limitations on the technical solutions of this application. In the absence of conflict, the embodiments of this application and the technical features in the embodiments can be combined with each other.

[0025] As shown in Figure 1, a first aspect of this application provides an air intake structure for a compressor. This air intake structure includes a horizontally split air intake section 1 and a rigid support section 2. Specifically, the horizontally split air intake section 1 includes a separable first bearing housing (e.g., an upper bearing housing) and a second bearing housing (e.g., a lower bearing housing). The first and second bearing housings meet along their horizontal mid-sections to form a guide cavity for guiding airflow into the compressor. The rigid support section 2 is an integrally cast or welded cylindrical structure with multiple adjustable guide vanes 18 arranged circumferentially inside to control the airflow rate and angle entering the compressor. The inlet end of the rigid support section 2 is fixedly connected to the outlet end of the guide cavity, and a first stop 3 is provided at the interface between them. Through this connection method, the highly rigid rigid support section 2 provides strong radial support and axial restraint for the split horizontally split air intake section 1.

[0026] In this technical solution, the first and second bearing housings are preferably made of ductile iron (such as QT400-18). This material has good casting fluidity, enabling the formation of complex flow channel structures, and its excellent shock absorption performance can effectively absorb the vibrations generated by the compressor operation. The first and second bearing housings are connected by a precision-machined center-part flange 16 and several high-strength bolts. To ensure the airtightness of the low-pressure area, a sealing groove is provided on the contact surface between the two, and a special liquid sealant is applied during assembly. The rigid support section 2, as the main load-bearing component, can be made of high-strength cast steel (such as ZG230-450) or welded from high-quality steel plates. Its axial length is not a fixed value, but is determined according to the installation span of the guide vane 18 mechanism and the airflow channel design requirements. In a specific design example, this axial length can be designed to be 300mm to 600mm.

[0027] Understandably, the horizontally split intake section 1 employs a split bearing housing structure, which greatly facilitates the maintenance and disassembly of internal components such as bearings and seals. However, under high-pressure conditions, this split structure is prone to radial expansion and deformation of the split surface due to internal pressure, leading to seal failure and gas leakage. To address this inherent defect, this application innovatively incorporates a rigid support section 2. This rigid support section 2 utilizes the inherent high rigidity of its integrated cylindrical structure and, through the precise engagement of the first stop 3, forms a clamp-like support and limiting effect on the outlet end of the horizontally split intake section 1. When the internal pressure of the unit increases, attempting to radially expand the split intake section, the rigid support section 2 generates sufficient reaction force to effectively suppress its radial expansion, thereby preventing the split surface from opening due to deformation. This completely solves the problem of traditional horizontally split structures failing hydrostatic tests under high-pressure conditions, significantly improving the operational safety and reliability of the unit.

[0028] In one feasible embodiment, the air intake structure further includes a first flange 4 and a second flange 5. The first flange 4 is disposed at the inlet end of the rigid support section 2, and the second flange 5 is disposed at the outlet end of the guide cavity. The first stop 3 specifically includes a first convex stop disposed on the first flange 4, and a first concave stop disposed on the second flange 5 that mates with the first convex stop.

[0029] In this technical solution, the mating dimensions of the stop are strictly controlled to achieve precise positioning and effective load-bearing. The height of the first convex stop can be designed to be 3mm-8mm, for example, 5mm. The mating first concave stop is an annular groove of the same depth. The radial mating clearance between the first convex stop and the first concave stop is precisely controlled between 0.05mm-0.15mm, for example, 0.08mm. This small clearance ensures both smooth assembly and extremely high alignment accuracy. During assembly, the first convex stop is first inserted into the first concave stop to achieve pre-positioning of the two shell sections, and then the bolts between the first flange 4 and the second flange 5 are tightened.

[0030] Understandably, this embodiment achieves a quick and reliable connection between the two housing sections via the first flange 4 and the second flange 5. Furthermore, the interlocking of the convex and concave stop joints between the two flanges provides multiple beneficial effects: First, it achieves precise coaxial positioning of the horizontally split intake section 1 and the rigid support section 2, ensuring the coaxiality requirement of the rotor axis running through them and preventing rotor vibration caused by installation deviations. Second, the first stop joint 3 effectively shares the enormous internal pressure and external pipeline loads generated during compressor operation. These loads, originally borne entirely by the connecting bolts, are now mostly borne by the stop joint structure, significantly reducing the stress level of the connecting bolts. Finally, this stop joint structure forms a robust stop ring, effectively suppressing the tendency for radial misalignment and elliptical deformation of the upper and lower split housings under high pressure, further reducing the risk of leakage at the split surface and providing dual protection for the long-term stable operation of the unit.

[0031] In one feasible implementation, as shown in Figures 3-5, the intake structure further includes a guide vane seat 6, multiple first mounting holes, second mounting holes, a drive shaft 7, and a transmission assembly. The guide vane seat 6 is disposed inside the rigid support section 2, and a transmission cavity is formed between its outer periphery and the inner wall of the rigid support section 2. Multiple first mounting holes are arranged circumferentially along the guide vane seat 6, and the guide vane shafts of multiple guide vanes 18 are rotatably disposed in the corresponding first mounting holes, with the ends of the guide vane shafts extending into the transmission cavity. Second mounting holes are disposed on the side wall of the rigid support section 2. The drive shaft 7 is rotatably disposed within the second mounting holes, with its driving end extending into the transmission cavity and connected to one of the guide vane shafts. The drive shaft 7 is driven by a guide vane actuator 8. The transmission assembly is disposed within the transmission cavity and is connected to all guide vane shafts to synchronously drive all guide vane shafts to rotate around their own axes when the drive shaft 7 rotates.

[0032] In this technical solution, the guide vane seat 6 can be made of aluminum alloy or cast iron (such as HT250). The guide vane seat 6 is a cylindrical structure that fits with the inner wall of the rigid support section 2, and an annular groove is provided in the middle of the cylindrical structure along the circumferential direction. Therefore, when the guide vane seat 6 and the rigid support section 2 are coaxially arranged, an annular transmission cavity is formed between the outer circumference of the guide vane seat 6 and the inner wall of the rigid support section 2. The width of this cavity is usually designed to be 30mm-50mm to accommodate the transmission components. Multiple first mounting holes are evenly distributed along the circumference of the guide vane seat 6, and the number of first mounting holes corresponds one-to-one with the number of guide vanes 18. The guide vane shaft of the guide vane 18 is rotatably mounted in the corresponding first mounting hole through a self-lubricating bearing, and the end of the guide vane shaft extends into the transmission cavity. The drive shaft 7 passes through the second mounting hole on the side wall of the rigid support section 2. One end of the drive shaft 7, located outside the rigid support section 2, is connected to the power output end of the guide vane actuator 8 (such as an electric actuator or hydraulic cylinder) via a coupling or key to receive external driving force. The end of the drive shaft 7, i.e., the drive end located inside the transmission cavity, can be rigidly connected to the end of one of the guide vane shafts via a key or coupling sleeve; this guide vane shaft is the drive shaft. When the guide vane actuator 8 rotates and drives one of the guide vane shafts connected to it to rotate, all the guide vanes 18 can be driven to rotate synchronously through the transmission assembly.

[0033] Understandably, the above solution directly and rigidly connects and transmits the drive shaft 7 and the guide vane shaft within a closed transmission cavity, avoiding the need for complex linkage mechanisms on the outside of the casing. Compared to the traditional drive method that drives the guide vane 18 to rotate via external linkages, which typically requires through holes or complex sealing structures on multiple casing walls, this application uses a single drive shaft 7 that passes through the casing wall and integrates the complex transmission connection internally. This significantly reduces the number of openings and the sealing area on the casing wall, thereby significantly reducing the risk of high-pressure gas leakage and facilitating the successful completion of the hydrostatic test. At the same time, this design effectively improves the overall structural integrity, effectively resisting deformation under high pressure, solving the sealing failure problem caused by insufficient rigidity in traditional horizontally split structures, and significantly improving the sealing reliability and operational safety of the unit.

[0034] In one feasible embodiment, the transmission assembly includes a plurality of bevel gears 9 and a bevel gear ring 10. The plurality of bevel gears 9 are respectively disposed on each guide vane shaft, and the bevel gear ring 10 is sleeved on the outer periphery of the guide vane seat 6 and meshes with all of the plurality of bevel gears 9.

[0035] In this technical solution, multiple bevel gears 9 are respectively fixedly mounted on the ends of each guide vane 18 shaft that extend into the transmission cavity via flat keys or splines. The material of the bevel gears 9 can be 20CrMnTi steel, with a surface treated by carburizing and quenching to achieve a hardness of HRC58-62, ensuring wear resistance of the transmission. The bevel gear ring 10 is designed as an integral ring gear structure, with an internal tooth surface on its inner ring, meshing simultaneously with multiple bevel gears 9. There are two bevel gear rings 10, arranged face-to-face and both meshing with the bevel gears 9 mounted on each guide vane shaft. The transmission cavity is filled with grease or lubricated by oil spraying through an oil passage to ensure good operation of the gear pair.

[0036] Understandably, this internal gear transmission method has significant advantages such as extremely compact structure and high transmission accuracy. It integrates a complex motion synchronization mechanism within the annular space between the guide vane seat 6 and the housing, without adding any external dimensions. When a guide vane shaft (drive shaft) is driven to rotate by the drive shaft 7, the bevel gear 9 on it rotates accordingly, driving the meshing bevel gear ring 10 to rotate. The rotating bevel gear ring 10 then synchronously drives all other bevel gears 9 and guide vane shafts to rotate, thereby achieving precise and synchronous adjustment of the opening of all guide vanes 18. This transmission method has a fast response speed and good synchronization, completely avoiding problems such as jamming, wear, and environmental influences that are prone to occur in external linkage mechanisms. It greatly improves the reliability of the guide vane 18 adjustment mechanism, providing a solid guarantee for the compressor to achieve precise flow and operating condition regulation.

[0037] In one feasible embodiment, the guide vane seat 6 further includes a guide vane bushing 11, which is detachably disposed between the guide vane seat 6, the horizontally split air intake section 1 and the rigid support section 2. After the guide vane bushing 11 is disassembled, the components adjacent to the guide vane bushing 11 obtain axial or radial disassembly and assembly clearance space.

[0038] In this technical solution, the guide vane sleeve 11 is designed as an independent annular thin-walled component. Its axial thickness can be customized according to the actual disassembly and assembly space requirements. It is connected and positioned with the guide vane seat 6 and the intake section through a precision stop. During normal operation, it is part of the entire support structure, transmitting force and torque. When a major overhaul of the compressor is required, especially when it is necessary to disassemble and inspect the bearings and other components inside the first bearing housing (upper bearing housing), maintenance personnel do not need to hoist the heavy rigid support section 2 as a whole. They only need to pull out the guide vane sleeve 11 axially. At this time, the space originally occupied by the guide vane sleeve 11 becomes an operable clearance space. This allows the bearings and other components inside the first bearing housing to no longer be restricted by the axial length of the rigid support section 2. They can be easily moved away from the rigid support section 2 and the guide vane seat 6 by first lifting them upward to a certain height and then moving them to one side, thereby exposing the internal bearing assembly and facilitating subsequent inspection, maintenance, or replacement work.

[0039] Understandably, given the practical need for regular disassembly and inspection of core components such as bearings during compressor operation, the guide vane bushing 11 provided in this embodiment offers a solution. The guide vane bushing 11 resolves the conflict between the rigid support section 2 and the split bearing housing in terms of maintenance and disassembly. This solution, by adding a detachable guide vane bushing 11, facilitates the disassembly and assembly of internal components of the bearing housing while ensuring the overall structural rigidity and strength. This design solves the difficulties in maintenance and disassembly of split structures, simplifying complex and time-consuming large-scale hoisting operations into a few simple steps, improving equipment maintainability, shortening unit downtime for maintenance, and reducing maintenance costs.

[0040] In one feasible embodiment, the guide vane bushing 11 and the guide vane seat 6 are connected by a second stop 12. The second stop 12 includes a second concave stop provided on the end face of the guide vane bushing 11 and a second convex stop provided on the end face of the guide vane seat 6, and the second concave stop and the second convex stop cooperate with each other.

[0041] In this technical solution, the mating dimensions of the second stop 12 are precisely designed to ensure ease of assembly and disassembly and accurate repeatability. The height of the second convex stop can be designed to be 4mm-6mm, for example, 5mm, and the gap between its radial mating surface and the radial mating surface of the second concave stop is controlled between 0.02mm-0.08mm. This precise fit ensures that the guide vane bushing 11 can accurately return to its original position after each installation, ensuring the concentricity requirements of the guide vane 18 drive mechanism. Simultaneously, an annular sealing groove can be formed on the mating surface of the second stop 12, containing an O-ring seal to prevent leakage of lubricating medium from the transmission cavity or intrusion of external impurities.

[0042] It is understandable that this embodiment achieves a modular connection between the guide vane bushing 11 and the guide vane seat 6 through the precise design of the second stop 12. This fitting structure using the second stop 12 ensures the installation position accuracy of the guide vane bushing 11, preventing jamming of the guide vane 18 or a decrease in transmission efficiency due to assembly deviations. Furthermore, the second stop 12 structure can effectively withstand the shearing force and torque generated during operation. Therefore, this standardized and modular connection design makes on-site maintenance operations more standardized and convenient; even non-professionals can complete disassembly and assembly according to standard procedures, significantly improving the maintainability of the equipment and the reliability of on-site operations.

[0043] As shown in Figure 6, a compressor is provided according to a second aspect of the present application, including the intake structure described in any of the above technical solutions, and also including a compressor main housing 13. The compressor main housing is connected to the outlet end of the rigid support section 2, and a mutually fitting third stop 14 is provided at the connection interface. The third stop 14 includes a third convex stop provided on the end face of the compressor main housing 13, and a third flange is provided at the outlet end of the rigid support section 2, with a third concave stop provided on the third flange, the third concave stop cooperating with the third convex stop.

[0044] In this technical solution, the design parameters of the third stop 14 are optimized according to the compressor's specifications and pressure rating. For large high-pressure compressors, the height of the third convex stop can be designed to be 8mm-15mm, with the mating clearance controlled between 0.05mm-0.12mm to ensure precise alignment under immense internal pressure. The thickness of the third flange is optimized through finite element analysis to ensure sufficient rigidity and strength under the combined action of bolt preload and internal pressure. The bolts connecting the third flange to the compressor housing 13 are preloaded using a hydraulic tensioner to ensure uniform preload force and improve connection reliability.

[0045] Understandably, this embodiment achieves uniform rigidity and sealing of the entire compressor unit by precisely connecting the high-rigidity intake structure to the compressor housing 13. This fitting structure via the third stop 14 ensures precise coaxiality between the intake section and the housing, allowing the rotor to operate smoothly and preventing rotor vibration and abnormal bearing wear caused by connection deviations. Secondly, the rigid connecting ring formed by the third stop 14 effectively transmits and disperses the enormous internal pressure load and pipeline thrust generated during compressor operation, preventing localized deformation caused by stress concentration. Furthermore, the combination of the third stop 14 and bolted connections creates multiple sealing guarantees, ensuring good airtightness at the connection interface even under the highest operating pressure, effectively preventing high-pressure gas leakage. This modular connection design simplifies compressor assembly; each functional module can be manufactured and tested independently, then precisely assembled on-site, significantly improving manufacturing and installation efficiency.

[0046] As shown in Figure 7, in one feasible embodiment, the compressor main casing has a horizontally split structure, including a first casing and a second casing that fit together, both with a center-parting flange 16 at the joint. A circumferential flange 15 is located at the outlet end of the compressor main casing, and the outer diameter of the circumferential flange 15 is larger than the outer diameter of the center-parting flange 16. Multiple bolt holes are provided on the center-parting flange 16, with the bolt holes located near the root of the circumferential flange 15.

[0047] In this technical solution, the outer diameter of the circumferential flange 15 is typically 15%-25% larger than in conventional designs. For example, for a compressor with an outlet diameter of 600mm, the outer diameter of the circumferential flange 15 can be increased from the conventional 800mm to 950mm. The distance between the centerline of the bolt holes on the split flange 16 and the root of the circumferential flange 15 is minimized, typically only 0.8-1.2 times the bolt hole diameter. For example, for M36 bolt holes, this distance can be designed to be 35mm-45mm. This extremely close design fully utilizes the high stiffness characteristics of the root region of the circumferential flange 15. The root of the circumferential flange 15 is the area connected to the main casing, possessing the largest moment of inertia and bending stiffness.

[0048] Understandably, this embodiment solves the problem of sealing the split face of a horizontally split housing under high-pressure water pressure testing through this structural layout, especially for large housings made of materials such as ductile iron (e.g., QT400-18). By increasing the outer diameter of the circumferential flange 15 and moving its engagement position outward, it is equivalent to increasing the lever arm and improving the connection stiffness, allowing the circumferential flange 15 to more effectively clamp the housing outlet end. Secondly, by bringing the bolt holes on the split face flange 16 closer to the root limit of the circumferential flange 15, the clamping force of the bolts can directly act on the area with the highest stiffness, greatly enhancing the bending resistance and tightness of the split face flange 16. When internal pressure attempts to separate the split face, this layout can generate the maximum resisting moment, effectively suppressing the opening of the split face. Therefore, this design fundamentally solves the sealing failure problem caused by insufficient connection rigidity due to the unreasonable layout of traditional bolt holes. Without increasing the flange thickness or using higher strength materials, it can significantly improve the pressure resistance and sealing reliability of the casing, ensuring the smooth passage of the hydrostatic test and providing structural protection for the long-term safe operation of the compressor under high pressure conditions.

[0049] Figure 8 shows a simulation diagram of the sealing effect of the imported casing under high-pressure hydrostatic testing before the improvement; Figure 9 shows a simulation diagram of the sealing effect of the imported casing of the present invention under high-pressure hydrostatic testing. Comparing Figures 8 and 9, it can be seen that under the same test pressure conditions, the structure before the improvement (Figure 8) shows obvious stress concentration and insufficient contact pressure in the center flange area (yellow area indicated by the arrow), indicating a risk of leakage in this area. However, after adopting the solution of the present invention (Figure 9), by increasing the outer diameter of the circumferential flange and bringing the horizontal flange mating hole closer to the root limit of the circumferential flange, the stress distribution in the center flange area is significantly improved, the original yellow low-pressure area disappears, and the contact pressure of the sealing surface is uniform and sufficient. The simulation results verify the effectiveness of the technical solution of the present invention in improving sealing performance and ensure the successful completion of the high-pressure hydrostatic test.

[0050] In one feasible implementation, as shown in Figure 2, the third flange is connected to the compressor housing 13 by a plurality of circumferentially distributed bolts, and the fastening nuts of the bolts located in the mounting area of ​​the guide vane actuator 8 are type II hexagonal nuts 17.

[0051] In this technical solution, to address the issue of limited installation space for the guide vane actuator 8 and interference between ordinary cap nuts and the bracket, the cap nuts corresponding to the installation area of ​​the guide vane actuator 8 are replaced with Type II hexagonal nuts 17. Since the required preload torque for the bolts in this location is relatively low, the Type II hexagonal nuts 17 effectively avoid interference while ensuring a tighter fit, thus facilitating the installation of the guide vane actuator 8.

[0052] Understandably, this embodiment upgrades the fasteners in the critical mounting area of ​​the guide vane actuator 8 by selecting Type II hexagonal nuts 17, achieving its connection advantages with minimal cost investment. Type II hexagonal nuts 17 provide a stronger and larger bearing surface, thus providing stronger preload and excellent anti-loosening performance, ensuring that the connecting bolts always maintain sufficient clamping force under long-term complex vibration environment, thereby directly guaranteeing the absolute reliability of the connection between the rigid support section 2 and the main housing.

[0053] In one feasible embodiment, the compressor further includes a rotor disposed within the compressor housing 13; the rotor has a smooth shaft section corresponding to the rigid support section 2, providing clearance space during axial advancement installation of the guide vane seat 6 and / or the guide vanes. The main purpose of this design is to provide the necessary clearance space when the guide vane seat 6 and / or the guide vanes 18 need to be axially advanced for installation or removal, avoiding motion interference between the rotor and these stationary components.

[0054] In this technical solution, the shaft segment corresponding to the rigid support section 2 of the rotor is machined into a precisely straight optical shaft. In conventional designs, this shaft segment may have structures such as shaft shoulders, sealing teeth, or balance discs, but in this embodiment, these functional components are relocated to other shaft segments. To compensate for any potential loss in airflow guidance function, the arc transition section of the airflow channel is provided on the shaft end seal or other stationary components, which provide a smooth airflow transition surface to ensure smooth gas flow.

[0055] Understandably, this embodiment, through the design of a partially straight optical axis on the rotor, firstly creates ample space for the axial advancement and installation of the guide vane seat 6 and the guide vane 18. During final assembly, the guide vane seat 6 and the guide vane 18 can be pushed axially into the rigid support section 2 as a whole module, and then circumferentially positioned and fixed after they are in place. This installation method is simpler and more efficient than the traditional radial assembly. Secondly, when the guide vane 18 needs to be replaced during maintenance, there is no need to disassemble the rotor; simply pull out the guide vane seat 6 module axially, greatly simplifying the maintenance process and shortening downtime. This design in this embodiment fully embodies the systematic and integrated design concept, achieving a perfect unity of assembly processability and operational reliability. Therefore, in this technical solution, the rotor is designed with a straight optical axis on the corresponding shaft section of the rigid support section, which not only avoids interference during guide vane seat installation but also ensures smooth airflow because the airflow transition function is undertaken by the shaft end sealing component.

[0056] In this invention, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "install," "connect," "link," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "link" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0057] In the description of this invention, it should be understood that the terms "upper," "lower," "left," "right," "front," "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or unit referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0058] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0059] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An intake structure for a compressor, characterized in that, include: The horizontally split intake section includes a separable first bearing housing and a second bearing housing, which are joined together to form a guide cavity for air intake; a rigid support section is an integral cylindrical structure, and multiple guide vanes are arranged circumferentially inside the rigid support section; the inlet end of the rigid support section is connected to the outlet end of the guide cavity, and a first stop is provided at the connection interface to provide rigid support for the horizontally split intake section.

2. The intake structure for a compressor according to claim 1, characterized in that, Also includes: A first flange is disposed at the inlet end of the rigid support section; a second flange is disposed at the outlet end of the guide cavity; the first stop includes a first convex stop disposed on the first flange, and a first concave stop disposed on the second flange that mates with the first convex stop.

3. The intake structure for a compressor according to claim 1, characterized in that, Also includes: A guide vane seat is disposed on the inner side of the rigid support section, and a transmission cavity is formed between the outer periphery of the guide vane seat and the inner wall of the rigid support section. Multiple first mounting holes are arranged circumferentially along the guide vane seat, and the guide vane shafts of multiple guide vanes are rotatably disposed in the corresponding first mounting holes, with the ends of the guide vane shafts extending into the transmission cavity; second mounting holes are disposed on the sidewall of the rigid support section; a drive shaft is rotatably disposed in the second mounting holes, with the end of the drive shaft extending into the transmission cavity, the drive end of the drive shaft being connected to one of the guide vane shafts, and the drive shaft being driven by a guide vane actuator; a transmission assembly is disposed in the transmission cavity, and the transmission assembly is respectively connected to all the guide vane shafts so as to drive all the guide vane shafts to rotate around their own axes when the drive shaft rotates.

4. The intake structure for a compressor according to claim 3, characterized in that, The transmission assembly includes: a plurality of bevel gears, each correspondingly disposed on each of the guide vane shafts; and a bevel gear ring, sleeved on the outer periphery of the guide vane seat, wherein the bevel gear ring meshes with all of the plurality of bevel gears.

5. The intake structure for a compressor according to claim 3, characterized in that, The guide vane seat also includes a guide vane bushing, which is detachably disposed between the guide vane seat, the horizontally split air intake section, and the rigid support section.

6. The intake structure for a compressor according to claim 5, characterized in that, The guide vane bushing and the guide vane seat are connected by a second stop; the second stop includes a second concave stop provided on the end face of the guide vane bushing and a second convex stop provided on the end face of the guide vane seat, and the second concave stop and the second convex stop cooperate with each other.

7. A compressor, characterized in that, The air intake structure, including any one of claims 1-6, further includes: a compressor main housing, wherein the compressor main housing is connected to the outlet end of the rigid support section, and a mutually fitting third stop is provided at the connection interface; the third stop includes a third convex stop provided on the end face of the compressor main housing, and a third flange is provided at the outlet end of the rigid support section, wherein a third concave stop is provided on the third flange, and the third concave stop cooperates with the third convex stop.

8. The compressor according to claim 7, characterized in that, The compressor main casing has a horizontally split structure, including a first casing and a second casing that fit together. A center-part flange is provided at the joint between the first casing and the second casing. A circumferential flange is provided at the outlet end of the compressor main casing. The outer diameter of the circumferential flange is larger than the outer edge diameter of the center-part flange. Multiple bolt holes are provided on the center-part flange, and the bolt holes are located near the root of the circumferential flange.

9. A compressor according to claim 7, characterized in that, The third flange is connected to the compressor housing by a plurality of circumferentially distributed bolts, and the bolts located in the guide vane actuator mounting area are type II hexagonal nuts.

10. A compressor according to claim 7, characterized in that, It also includes a rotor, which is disposed within the compressor housing; the rotor has a smooth shaft section corresponding to the rigid support section, which provides clearance space when the guide vane seat and / or the guide vane are axially advanced and installed.

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